Pre-rectified distributors, heat exchanger assemblies and refrigeration equipment

Abstract

This invention provides a pre-rectifying distributor, a heat exchanger assembly, and a refrigeration device. The pre-rectifying distributor includes a main body and a flow pattern sculptor, a jetting component, and a reflective mixing guide plate sequentially disposed within the inner cavity of the main body along the refrigerant flow direction. The flow pattern sculptor and the liquid inlet end of the main body enclose a pre-rectifying cavity, and the flow pattern sculptor and the jetting component enclose a flow pattern maintaining cavity. The flow pattern sculptor has multiple liquid passage holes distributed around the outer periphery of the projection area of ​​the liquid inlet pipe assembly hole on the flow pattern sculptor. The jetting component has a jetting hole communicating with the flow pattern maintaining cavity, and the jetting hole is opposite to the projection area of ​​the liquid inlet pipe assembly hole on the flow pattern sculptor. The reflective mixing guide plate and the jetting component enclose a reflective mixing cavity, and the jetting component and the main body liquid outlet end enclose a distribution cavity. The reflective mixing guide plate has multiple guide holes corresponding one-to-one with the multiple distribution holes, and the multiple guide holes are distributed in a ring around the axis of the main body around the outer periphery of the projection area of ​​the jetting hole on the reflective mixing guide plate.

Description

Technical Field

[0001] This invention relates to the field of refrigerant distribution technology, and particularly to a pre-rectified distributor, heat exchanger assembly, and refrigeration equipment. Background Technology

[0002] With the development of small-diameter pipe technology, evaporative heat exchangers in refrigeration and air conditioning systems often adopt multi-flow-path designs to reduce refrigerant pressure drop and improve heat exchange performance. To ensure that the throttled gas-liquid two-phase refrigerant is evenly distributed into each flow path of the evaporator, a distributor needs to be introduced before the evaporator. However, due to space limitations of the indoor unit, the two-phase refrigerant after throttling by the expansion valve must be redirected through a bent inlet connecting pipe before entering the distributor. When the refrigerant passes through the bent section of the inlet connecting pipe, the liquid phase, due to its higher density and viscosity, experiences a greater centrifugal force than the gaseous phase, causing the liquid refrigerant to accumulate on the outside of the bent section, while the gaseous phase accumulates on the inside. This gas-liquid separation leads to an asymmetrical flow pattern of the two-phase refrigerant entering the distributor body, which severely affects the uniformity of the distributor.

[0003] To address this issue, some have proposed making continuous reverse bends on the inlet connecting pipe or adjusting the necessary straight section length after the bends to improve the degree of gas-liquid phase separation, such as... Figure 1A As shown. However, both continuous reverse bending and increased straight section length after bending increase the installation space of the inlet connecting pipe. Bending parameters or necessary straight section parameters need to be customized and verified according to the different model sizes in actual applications. Such improvement solutions are obviously uneconomical in terms of uncertainty and workload in practical applications, and may not even be applicable to some models with limited space, such as 1HP or 1.5HP household air conditioner indoor units. Furthermore, continuous reverse bending can also lead to problems such as excessive inlet refrigerant pressure loss, excessive noise, and difficulty in ensuring the precision and consistency of batch processing.

[0004] In addition, some have proposed machining a jet section with a reduced inner diameter in the middle region of the brass distributor inlet pipe, hoping to increase the refrigerant flow rate through the jet section, thereby improving the mixing uniformity of the gas-liquid two-phase refrigerant. Figure 1A and Figure 1B As shown. However, considering the control of pressure loss during refrigerant transmission, relying solely on throttling and speed-up to improve the uniformity of refrigerant mixing between the two phases is very limited. Furthermore, currently, the upper jet section of brass distributors can only be formed using metal cutting, a method that is not only difficult and costly to machine, but also struggles to guarantee consistency after machining, thus greatly limiting the application of this type of distributor. Summary of the Invention

[0005] In order to overcome at least one deficiency of the prior art, the present invention provides a pre-rectified distributor, a heat exchanger assembly, and a refrigeration device.

[0006] To achieve the above objectives, the present invention provides a pre-rectification distributor, comprising a body and a flow pattern sculptor, a jetting component, and a reflective mixing guide plate sequentially disposed within the inner cavity of the body along the refrigerant flow direction. The liquid inlet end of the body has a liquid inlet pipe assembly hole, and its liquid outlet end has multiple distributing holes. The flow pattern sculptor and the liquid inlet end of the body enclose a pre-rectification cavity, and the flow pattern sculptor and the jetting component enclose a flow pattern maintaining cavity. The flow pattern sculptor has multiple liquid passage holes communicating with the pre-rectification cavity and the flow pattern maintaining cavity, and these multiple liquid passage holes are distributed around the outer periphery of the projection area of ​​the liquid inlet pipe assembly hole on the flow pattern sculptor. The jetting component has a jetting hole communicating with the flow pattern maintaining cavity, and the jetting hole is opposite to the projection area of ​​the liquid inlet pipe assembly hole on the flow pattern sculptor. The reflective mixing guide plate and the jet component form a reflective mixing cavity that connects to the jet hole, and the liquid outlet end of the main body forms a flow separation cavity. The reflective mixing guide plate has multiple guide holes that correspond one-to-one with the multiple liquid separation holes and connect to the reflective mixing cavity and the flow separation cavity respectively. The multiple guide holes are distributed in a ring around the axis of the main body on the outer periphery of the projection area of ​​the jet hole on the reflective mixing guide plate.

[0007] According to an embodiment of the present invention, the pre-rectification cavity volume V1, the flow pattern maintenance cavity volume V2, and the reflection mixing cavity volume V3 satisfy the following: 0.6≤V1 / V2≤1.5, 0.6≤V2 / V3≤1.5.

[0008] According to an embodiment of the present invention, a finishing cavity with an opening facing the liquid inlet pipe assembly hole is formed in the area opposite to the liquid inlet pipe assembly hole on the flow pattern finishing component. The longitudinal cross-sectional outline of the finishing cavity is one or more combinations of square, trapezoidal, triangular or partially circular.

[0009] Alternatively, the flow pattern finishing component is a plate structure in which both the upstream and downstream surfaces are nearly planar.

[0010] According to one embodiment of the present invention, the flow-patterning member at the concave cavity protrudes and extends toward the side where the jet member is located.

[0011] According to an embodiment of the present invention, the pre-rectified distributor further includes a partition disposed between the flow pattern rectifier and the jetting component. The partition divides the flow pattern maintaining cavity into a first maintaining cavity and a second maintaining cavity. A plurality of partition holes are formed on the partition to connect the first maintaining cavity and the second maintaining cavity. The pre-rectified cavity volume V1, the first maintaining cavity V21 and the second maintaining cavity V22 satisfy the following: 0.75≤V1 / V21≤1.3, 0.75≤V21 / V22≤1.3.

[0012] According to one embodiment of the present invention, the plurality of baffle holes and the plurality of liquid passage holes on the flow pattern finishing component are staggered, and the sum of the flow areas S2 of the plurality of baffle holes and the cross-sectional area S02 of the inner cavity of the body where the baffle is located satisfy the following condition: 0.1≤S2 / S02≤0.45.

[0013] According to an embodiment of the present invention, on the flow pattern finishing member, the area opposite to the liquid inlet pipe assembly hole protrudes and extends toward the side where the jet member is located to form a finishing cavity with an opening facing the liquid inlet pipe assembly hole, and a clearance hole is formed on the partition plate opposite to the finishing cavity, and the partition plate is sleeved on the outer periphery of the finishing cavity through the clearance hole.

[0014] Alternatively, the partition plate may have a closed structure opposite to the tidying cavity, with the partition plate basically fitting against the outer bottom surface of the tidying cavity.

[0015] According to an embodiment of the present invention, the sum of the flow areas S1 of the plurality of liquid passage holes on the flow patterning component and the cross-sectional area S01 of the body receiving cavity where the flow patterning component is located satisfy the following condition: 0.1≤S1 / S01≤0.45.

[0016] According to one embodiment of the present invention, the liquid passage holes on the flow pattern finishing component and the flow guide holes on the reflective mixing guide plate are one or more combinations of through holes, flanged holes, and arc bubble holes; the flow holes on the jet component are through holes or flanged holes whose hole walls extend in the direction of the reflective mixing guide plate.

[0017] According to one embodiment of the present invention, a mixing cavity with an opening facing the jet hole is formed in the region opposite to the jet hole on the reflective mixing guide plate, and the longitudinal cross-sectional profile of the mixing cavity is one or more combinations of square, trapezoidal, triangular or partially circular.

[0018] According to one embodiment of the present invention, the reflective mixing guide plate at the mixing cavity protrudes and extends towards the liquid outlet end of the body, and an annular flow divider is formed between the downstream surface of the mixing cavity and the inner peripheral wall of the body.

[0019] According to an embodiment of the present invention, when the longitudinal cross-sectional profile of the mixing cavity is square or trapezoidal, the vertical distance H from the extended top of the mixing cavity to the inner bottom wall of the liquid outlet of the body satisfies: 0≤H≤3mm.

[0020] According to an embodiment of the present invention, the downstream surface of the reflective mixing guide plate is close to a plane. The pre-rectified distributor further includes a flow channel forming member disposed in the flow distribution cavity and located on the inner periphery of multiple liquid distribution holes. The flow channel forming member is a rotating member that extends protruding from the inner bottom wall of the liquid outlet end of the body towards the direction of the reflective mixing guide plate and rotates around the axis of the body. An annular flow channel connecting multiple liquid distribution holes is formed between the flow channel forming member and the inner peripheral wall of the body. The cross-section of the flow channel forming member remains basically unchanged or gradually decreases with the extension direction.

[0021] According to one embodiment of the present invention, the flow channel forming member is a spacer with a cross-section that remains substantially unchanged along its extension direction, and the extended top end of the spacer abuts against the reflective mixing guide plate region of the inner periphery of a plurality of guide holes.

[0022] According to an embodiment of the present invention, the cross-section of the flow channel forming member gradually decreases along its extension direction, and the vertical distance H1 from the extension tip of the flow channel forming member to the downstream surface of the reflective mixing guide plate satisfies: 1mm≤H1≤2H0 / 3, where H0 is the height of the flow splitting cavity.

[0023] According to one embodiment of the present invention, the pre-rectified distributor further includes an inlet pipe welded to the inlet pipe assembly hole, the inlet pipe including a main body section with a substantially constant inner diameter and a jet section with a smaller inner diameter than the main body section, which are distributed sequentially along the refrigerant flow direction.

[0024] According to one embodiment of the present invention, the inner diameter of the liquid outlet end of the jet orifice on the jetting element is less than or equal to the minimum inner diameter of the jetting section on the inlet pipe.

[0025] According to one embodiment of the present invention, a jet orifice plate is provided inside the liquid inlet pipe. The jet orifice plate has jet orifice holes with an inner diameter smaller than that of the main body section. The jet orifice holes are through holes or flanged holes. The location of the jet orifice plate forms the jet section of the liquid inlet pipe.

[0026] Alternatively, the jet section can be a Venturi tube section, with the throat of the Venturi tube section being the point of minimum inner diameter of the jet section.

[0027] Alternatively, the jet section can be a straight section with a reduced inner diameter relative to the main body section.

[0028] According to an embodiment of the present invention, the pre-rectified distributor further includes multiple branch pipes welded and connected to multiple dispensing holes respectively. Each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section with an inner diameter that is smaller than the inner diameter at the downstream end of the first pipe section. The difference Δd between the inner diameter d11 at the downstream end of the first pipe section and the inner diameter d12 at the downstream end of the second pipe section is: 0.1mm≤Δd≤3.5mm.

[0029] According to an embodiment of the present invention, a reflective section is formed on the first pipe section, which bends and extends to one side relative to the center line of the dispensing hole. The axis at the upstream end of the reflective section and the axis at the downstream end of the reflective section intersect to form an angle θ, and 90°≤θ≤175°. Based on the reflective section, the axis of the second pipe section intersects the center line of the dispensing hole.

[0030] Alternatively, the first pipe section can be a straight pipe.

[0031] According to one embodiment of the present invention, each branch pipe further includes a branch section, the second pipe section is a tapered structure integrally formed with the first pipe section and the inner diameter gradually decreases, the branch section is welded to the second pipe section, or the first pipe section, the second pipe section and the branch section are integrally formed.

[0032] Alternatively, the branch section can be sleeved and welded to the first pipe section, and the sleeved and welded joint between the two forms the second pipe section;

[0033] Alternatively, the branch section is welded to the first pipe section, and the second pipe section is formed from the branch section.

[0034] On the other hand, the present invention also provides a pre-rectification distributor, comprising: a body and a flow pattern sizing member, a jetting member, and a flow channel forming member sequentially disposed within a cavity of the body along the refrigerant flow direction. The body has an inlet pipe assembly hole at its inlet end and multiple distributing holes at its outlet end. The flow pattern sizing member and the inlet end of the body enclose a pre-rectification cavity, and the flow pattern maintaining cavity is formed between the flow pattern sizing member and the jetting member. The flow pattern sizing member has multiple liquid passage holes communicating with the pre-rectification cavity and the flow pattern maintaining cavity, and these multiple liquid passage holes are distributed around the outer periphery of the projection area of ​​the inlet pipe assembly hole on the flow pattern sizing member. The jetting member has a jetting hole communicating with the flow pattern maintaining cavity, and the jetting hole is opposite to the projection area of ​​the inlet pipe assembly hole on the flow pattern sizing member. The flow channel forming element is disposed between the jet element and the liquid outlet end of the body and is located on the inner circumference of multiple liquid distribution holes. The flow channel forming element is a rotating element that extends from the inner bottom wall of the liquid outlet end of the body towards the direction of the jet element and rotates around the axis of the body. The jet element, the flow channel forming element and the liquid outlet end of the body form an annular flow distribution cavity that connects multiple liquid distribution holes. The cross-section of the flow channel forming element remains basically unchanged or gradually decreases with the extension direction.

[0035] According to an embodiment of the present invention, the pre-rectification cavity volume V1, the flow pattern maintenance cavity volume V2, and the annular shunt cavity volume V4' satisfy the following: 0.6≤V1 / V2≤1.5, 0.6≤V2 / V4'≤1.5.

[0036] According to an embodiment of the present invention, the pre-rectified distributor further includes a partition disposed between the flow pattern sizing member and the jet member. The partition divides the flow pattern maintaining chamber into a first maintaining chamber and a second maintaining chamber. The partition has a plurality of partition holes that connect the first maintaining chamber and the second maintaining chamber, and the plurality of partition holes are staggered with a plurality of liquid passage holes on the flow pattern sizing member. The pre-rectified chamber volume V1, the first maintaining chamber V21 and the second maintaining chamber V22 satisfy the following: 0.75≤V1 / V21≤1.3, 0.75≤V21 / V22≤1.3.

[0037] On the other hand, the present invention also provides a heat exchanger assembly, characterized in that it includes any of the above-mentioned pre-rectified distributors.

[0038] On the other hand, the present invention also provides a refrigeration device including the above-described heat exchanger assembly.

[0039] In summary, the pre-rectified distributor provided by this invention features a flow pattern sculptor on the side of the internal cavity near the liquid inlet. This flow pattern sculptor reflects the gas-liquid two-phase separated refrigerant input from the liquid inlet, breaking the liquid film into droplets to promote gas-liquid mixing. Simultaneously, the refrigerant reflection stream and incident stream, moving in opposite directions, create turbulence within the pre-rectified cavity enclosed by the flow pattern sculptor and the liquid inlet of the main body, enhancing the turbulence of the two-phase flow and causing the refrigerant to gradually develop into a dispersed flow pattern. The pre-rectified refrigerant enters the flow pattern maintenance cavity, where it is fully mixed and develops before converging at the jet orifice on the jetting element. The jet orifice reduces the pressure and increases the speed of the refrigerant flow, increasing the refrigerant velocity so that the liquid refrigerant has sufficient inertial force to overcome gravity during subsequent distribution, preventing gas-liquid two-phase segregation from recurring in the fully mixed dispersed flow pattern and improving the uniformity of refrigerant distribution. Furthermore, by precisely controlling the volume ratio of the pre-rectification cavity, the flow pattern maintenance cavity, and the reflection mixing cavity within the main body, the refrigerant can fully develop into a stable diffuse flow pattern in the flow pattern maintenance cavity and maintain this flow pattern throughout the distribution process after jetting, thereby significantly improving the distribution performance of the distributor.

[0040] The pre-rectified distributor provided by this invention achieves pre-rectification of the inlet refrigerant flow pattern by incorporating flow pattern shaping and jetting components within the main body, thereby reducing the impact of the refrigerant inlet flow pattern on distribution performance. This distributor structure eliminates the need for any adjustments to the inlet pipe, greatly simplifying the processing, installation, and welding of the inlet pipe, and significantly improving the distributor's applicability to ensure compatibility with various refrigeration equipment specifications.

[0041] To make the above and other objects, features and advantages of the present invention more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0042] Figure 1A The diagram shows a liquid inlet pipe structure in the prior art where multiple bends are provided on the liquid inlet pipe to improve the refrigerant flow pattern at the distributor inlet.

[0043] Figure 1B The diagram shows the existing brass shunt structure.

[0044] Figure 2 The diagram shown is a structural schematic of the pre-rectified distributor provided in Embodiment 1 of the present invention.

[0045] Figure 3 As shown Figure 2 A schematic diagram showing the distribution of the pre-rectifier cavity volume, the flow pattern maintenance cavity volume, and the reflection mixing cavity volume.

[0046] Figure 4 As shown Figure 2A schematic diagram of the structure of a medium-flow finishing component.

[0047] Figure 5A , Figure 5B , Figure 5C , Figure 5D as well as Figure 5E The diagram shown is a structural schematic of a flow pattern finishing component provided in another embodiment of the present invention.

[0048] Figure 6A and Figure 6B The diagram shown is a schematic diagram of the jet component in a pre-rectified distributor provided in another embodiment of the present invention.

[0049] Figure 7 As shown Figure 2 A schematic diagram of the structure of the mid-reflection hybrid guide plate.

[0050] Figure 8 The diagram shown is a schematic diagram of the pre-rectified distributor after removing the inlet pipe and branch pipe according to another embodiment of the present invention.

[0051] Figure 9A and Figure 9B The diagram shown is a schematic diagram of the inlet pipe in a pre-rectified distributor provided in another embodiment of the present invention.

[0052] Figure 9C The diagram shown is a structural schematic of a pre-rectified distributor provided in another embodiment of the present invention.

[0053] Figure 10 As shown Figure 2 A schematic diagram of the structure of the central branch pipe.

[0054] Figure 11A , Figure 11B , Figure 11C , Figure 11D , Figure 11E , Figure 11F as well as Figure 11G This is a schematic diagram of the branch pipe structure in a pre-rectified distributor provided in another embodiment of the present invention.

[0055] Figure 12 The diagram shown is a structural schematic of the pre-rectified distributor provided in Embodiment 2 of the present invention.

[0056] Figure 13 As shown Figure 12 A schematic diagram of the structure after removing the inlet pipe and branch pipe.

[0057] Figure 14A , Figure 14B , Figure 14C as well as Figure 14D The diagram shown is a structural schematic of the flow pattern sculptor in a pre-rectified distributor provided in another embodiment of the present invention.

[0058] Figure 15 The diagram shown is a structural schematic of the pre-rectified distributor provided in Embodiment 3 of the present invention.

[0059] Figure 16 As shown Figure 15 A schematic diagram of the structure after removing the inlet pipe and branch pipe.

[0060] Figure 17 As shown Figure 15 A schematic diagram of the structure of the partition plate.

[0061] Figure 17A The diagram shows a projection of multiple liquid passage holes on a baffle plate on a flow pattern finishing component.

[0062] Figure 18A , Figure 18B as well as Figure 18C The diagram shown is a schematic diagram of the pre-rectified distributor after removing the inlet pipe and branch pipe according to another embodiment of the present invention.

[0063] Figure 19 The diagram shown is a structural schematic of the pre-rectified distributor provided in Embodiment 4 of the present invention.

[0064] Figure 20 The diagram shown is a structural schematic of a pre-rectified distributor provided in another embodiment of the present invention.

[0065] Figure 21 The diagram shown is a structural schematic of the pre-rectified distributor provided in Embodiment 5 of the present invention. Detailed Implementation

[0066] In this application, the distinction between upstream and downstream is based on the refrigerant flow direction. Generally, refrigerant flows from upstream to downstream, and the downstream area receives refrigerant from upstream. In refrigeration equipment, distributors are generally installed vertically or at an angle, with the liquid inlet of the distributor located below the liquid outlet along the direction of gravity. The inertial force of the refrigerant in the distributor overcomes gravity and flows in the opposite direction of gravity; in this case, upstream and downstream are still distinguished according to the refrigerant flow direction.

[0067] Example 1

[0068] The distributor connects the expansion valve and the heat exchanger assembly to evenly and equally distribute the throttled two-phase refrigerant to each branch of the heat exchanger assembly. This connection means that the distributor's performance is affected not only by its own structure but also by the upstream refrigerant flow state (i.e., inlet flow pattern) and downstream branch factors. Due to space constraints within the refrigeration equipment, a bent inlet connecting pipe is required between the expansion valve and the distributor's inlet. Because the gas and liquid phases experience different centrifugal forces at the bend, phase separation occurs at this point, leading to an asymmetrical flow pattern; this asymmetry is particularly pronounced at lower refrigerant mass flow rates. To address the inherent deficiencies in the refrigerant inlet flow pattern, existing distributors (such as...) Figure 1A and 1B As shown, it is extremely difficult to improve, which is the main limiting factor for further performance enhancement of existing distributors. Therefore, some have proposed improving the distributor inlet connection pipe to optimize the inlet flow pattern (such as...). Figure 1A (As shown in the figure), but this solution increases the installation space of the inlet connecting pipe, making it difficult to apply to refrigeration equipment with limited installation space; in addition, this optimization solution will also bring great difficulty to the processing and welding of the inlet connecting pipe.

[0069] In view of this, this embodiment provides a pre-rectified distributor that can sort and transform the inlet flow pattern before distribution. For example... Figure 2 As shown, the pre-rectifying distributor provided in this embodiment includes a body 1 and a flow pattern sculptor 2, a jetting component 3, and a reflective mixing guide plate 4, which are sequentially arranged in the inner cavity of the body 1 along the refrigerant flow direction. An inlet pipe assembly hole 13 is formed on the liquid inlet end 11 of the body, and multiple liquid distribution holes 14 are formed on its liquid outlet end 12. The flow pattern sculptor 2 and the liquid inlet end 11 of the body enclose a pre-rectifying cavity 101, and the flow pattern maintaining cavity 102 is enclosed between the flow pattern sculptor 2 and the jetting component 3. The flow pattern sculptor 2 has multiple liquid passage holes 21 connecting the pre-rectifying cavity 101 and the flow pattern maintaining cavity 102, and the multiple liquid passage holes 21 are distributed on the outer periphery of the projection area of ​​the liquid inlet pipe assembly hole 13 on the flow pattern sculptor 2. The jetting component 3 has a jetting hole 31 that connects to the flow pattern maintaining cavity 102, and the jetting hole 31 is opposite to the projection area of ​​the liquid inlet pipe assembly hole 13 on the flow pattern arranging component 2 (that is, when projected along the axial direction of the body, the jetting hole 31 is also located in the flow pattern arranging component area within the inner periphery of the multiple liquid passage holes 21). The reflective mixing guide plate 4 and the jetting component 3 form a reflective mixing cavity 103 that connects to the jetting hole 31, and the reflective mixing guide plate 4 and the liquid outlet end 12 of the body form a diversion cavity 104. The reflective mixing guide plate 4 has multiple guide holes 41 that correspond one-to-one with the multiple liquid diversion holes 14 and respectively connect to the reflective mixing cavity 103 and the diversion cavity 104. The multiple guide holes 41 are distributed in a ring around the axis of the body 1 on the outer periphery of the projection area of ​​the jetting hole 31 on the reflective mixing guide plate 4.

[0070] The pre-rectified distributor provided in this embodiment integrates the rectification and conversion of the inlet flow pattern and the uniform distribution of the refrigerant after conversion. The following will combine... Figures 2 to 10 The structure and working principle of the pre-rectified distributor provided in this embodiment are described in detail.

[0071] like Figure 2 As shown, due to the centrifugal force at the bend in the liquid inlet pipe 5, the refrigerant input into the body 1 through the liquid inlet pipe 5 exhibits an asymmetrical flow pattern with gas-liquid two-phase separation. After entering the body 1, the refrigerant is sprayed onto the flow pattern shaping element 2, and after being reflected by the flow pattern shaping element 2, it bounces back into the pre-rectification cavity 101 enclosed by the flow pattern shaping element 2 and the liquid inlet end 11 of the body. The reflection of the flow pattern shaping element 2 promotes the collision of the gas and liquid phases to initially disperse the liquid refrigerant into droplets; then, the refrigerant reflected stream and incident stream with opposite directions of movement form turbulence in the pre-rectification cavity 101, and the droplets are further dispersed and spread outwards. The dispersed droplets are distributed into the gas phase, causing the refrigerant to gradually develop into a uniformly mixed diffuse flow pattern. Afterwards, the refrigerant enters the flow pattern maintaining cavity 102 through multiple liquid passage holes 21 on the flow pattern shaping element 2. When the pre-rectified refrigerant passes through the liquid passage 21, the flow rate increases, the liquid phase mass flow rate increases with the increase of the liquid phase flow rate, and the liquid film becomes thinner; the thinned liquid film breaks down, causing the droplets to atomize into smaller shapes and be uniformly dispersed into the gas phase. The refrigerant gradually develops into a diffuse flow pattern in the flow pattern maintenance cavity 102, thereby realizing the rectification conversion from the inlet asymmetric flow pattern to a uniform diffuse flow pattern.

[0072] After the flow pattern conversion, the refrigerant needs to be evenly distributed into each branch pipe 6. Since the distributor is usually installed vertically, the refrigerant needs to be distributed from bottom to top into multiple branch pipes 6 in the opposite direction of gravity. During the distribution process, the refrigerant will be subjected to both inertial force and gravity. In a gas-liquid two-phase refrigerant, the flow of the liquid phase refrigerant mainly relies on inertial force and gravity. If the refrigerant flow rate is too low, the inertial force of the liquid phase refrigerant will be less than its gravity. After the flow pattern is adjusted, the liquid phase in the refrigerant is easily affected by gravity and separates from the gas phase again. In some cases, some refrigerant may even deposit and fail to be distributed to the liquid outlet side, which will seriously affect the uniformity of the distribution. In order to avoid gas-liquid two-phase segregation of the refrigerant after the flow pattern adjustment during the subsequent distribution process, this embodiment provides a jet hole 31 on the jet component 3. The refrigerant that has developed into a diffuse flow pattern in the flow pattern maintenance cavity 102 gradually gathers into the jet hole 31, and after being depressurized and accelerated by the jet hole 31, it is sprayed into the reflective mixing cavity 103. The high-speed refrigerant increases the inertial force of the liquid refrigerant, enabling it to overcome gravity and follow the gas phase flow, thus maintaining the two-phase refrigerant in a dispersed flow pattern as much as possible. The high-speed refrigerant entering the reflective mixing chamber 103 continues to flow forward under the influence of inertial force and impacts the reflective mixing guide plate 4. The reflective mixing guide plate 4 reflects the refrigerant, enhancing the collision degree between the gas and liquid phases. Simultaneously, the reflective stream and the jet stream undergo convection to further promote the mixing of the gas and liquid phases.

[0073] The mixed refrigerant is uniformly distributed into a plurality of guide holes 41 arranged in a ring around the axis of the main body 1. In this embodiment, a plurality of guide holes 41 are arranged in a ring at equal intervals on the reflective mixing guide plate 4, and the number of guide holes 41 is the same as the number of liquid distribution holes 14, and each guide hole 41 is substantially coaxial with its corresponding liquid distribution hole 14. This arrangement forms the shortest axial transmission path between the guide holes 41 and the liquid distribution holes 14, allowing the high-speed refrigerant output from the guide holes 41 to quickly enter the corresponding liquid distribution holes 14, maintaining the flow pattern of the mixed refrigerant as much as possible to ensure uniform distribution. In addition, in this embodiment, after the refrigerant is accelerated by the jet holes 31 and enters the reflective mixing cavity 103, a high-pressure vortex is formed on the downstream side of the jet element 3, which accelerates the refrigerant's entry into the guide holes 41.

[0074] This embodiment provides a pre-rectified distributor that replaces the existing inlet pipe bending scheme by optimizing the internal structure of the body 1. This transforms the asymmetrical flow pattern of the refrigerant inlet into a uniform, dispersed flow pattern, reducing the impact of the refrigerant inlet flow pattern on distribution performance. The refrigerant inlet flow pattern conversion achieved through body optimization makes the pre-rectified distributor highly compatible with various refrigerant inlet conditions and refrigeration equipment with different installation spaces. Specifically, the pre-rectified distributor eliminates the impact of the refrigerant inlet flow pattern on distributor performance, and the arrangement of the inlet-side piping no longer needs to consider the gas-liquid mixing of the refrigerant in the inlet pipe, thus greatly facilitating the processing, installation, and welding of the inlet-side piping. Furthermore, compared to the larger installation space required by bending the inlet pipe, the optimized internal structure of the distributor body 1 only slightly increases the axial length of the distributor body. Therefore, it is well-suited for refrigeration equipment with different installation spaces, including compact 1HP or 1.5HP household air conditioner indoor units.

[0075] A Froude number greater than 7, representing the ratio of the inertial force to gravity of the liquid refrigerant, is a condition for the refrigerant to develop into a stable, dispersed flow pattern. The inertial force of the liquid refrigerant is related to its flow velocity, which in turn is related to the volume of the chamber it occupies. Therefore, the volume of the pre-rectifying chamber V1 and the volume of the flow pattern maintaining chamber V2 are set to satisfy 0.6 ≤ V1 / V2 ≤ 1.5. This setting precisely controls the expansion degree of the refrigerant entering the flow pattern maintaining chamber 102, ensuring that the liquid phase of the refrigerant still has sufficient inertial force to overcome the influence of gravity after entering the flow pattern maintaining chamber 102, providing conditions for the refrigerant to fully mix and develop into a stable, dispersed flow pattern within the flow pattern maintaining chamber 102. Similarly, to avoid the refrigerant injected through the jet orifice 31 from excessively expanding and affecting its flow velocity after entering the reflective mixing chamber 103, the volume of the flow pattern maintaining chamber V2 and the volume of the reflective mixing chamber V3 are also set to satisfy 0.6 ≤ V2 / V3 ≤ 1.5. The ratio of the pre-rectification cavity volume V1, the flow pattern maintenance cavity volume V2, and the reflective mixing cavity volume V3 is set to ensure that the refrigerant maintains a uniform and stable dispersed flow pattern during both the flow pattern rectification stage and the post-rectification redistribution stage, thereby further improving the distribution uniformity. Preferably, 0.8 ≤ V1 / V2 ≤ 1.2 and 0.8 ≤ V2 / V3 ≤ 1.2 are set. However, the present invention does not impose any limitations on this.

[0076] Specifically, such as Figure 3 As shown, the pre-rectification cavity volume V1 refers to the volume of the chamber enclosed between the plane containing the upstream surface of the flow pattern rectifier 2 near the liquid passage 21 and the inner wall of the liquid inlet end 11 of the main body, such as... Figure 3 The volume of the cavity 101 enclosed by the dashed line. The flow pattern maintenance cavity volume V2 refers to the volume of the cavity enclosed between the plane containing the upstream surface of the jet component 3 and the downstream surface of the flow pattern finishing component 2, such as... Figure 3The volume of the cavity 102 enclosed by the dashed line at the midpoint. The volume V3 of the reflective mixing cavity refers to the volume of the cavity enclosed by the plane containing the upstream surface of the reflective mixing guide plate 4 near the guide hole and the downstream surface of the jet component 3, such as... Figure 3 The volume of chamber 103 enclosed by the dashed line.

[0077] In this embodiment, as Figure 4 As shown, the flow pattern setter 2 is a plate structure with nearly planar surfaces on both sides and a circular cross-section. However, the present invention does not limit this in any way. In other embodiments, the projection area of ​​the liquid inlet pipe assembly hole 13 on the flow pattern setter 2 can also be set into other shapes, such as... Figure 5A As shown, a finishing cavity 22 is formed. At this time, the downstream surface of the flow pattern finishing member 2 is still close to a plane.

[0078] In this embodiment, the sum of the flow areas S2 of the multiple liquid passages 21 on the flow pattern facilitator 2 and the cross-sectional area S02 of the body cavity where the flow pattern facilitator 2 is located satisfy the following ratio: 0.1 ≤ S2 / S02 ≤ 0.45. This area ratio limits the rate of refrigerant depressurization caused by the liquid passages 21, increases the refrigerant flow rate into the flow pattern maintenance cavity 102, and ensures that the refrigerant develops into a stable dispersed flow pattern while avoiding excessive refrigerant pressure loss due to excessive depressurization. Specifically, S2 / S02 can be set to area ratios such as 0.15, 0.2, 0.25, 0.3, and 0.35.

[0079] like Figure 4 As shown, in this embodiment, the liquid passage hole 21 on the flow pattern facilitator is a through hole with a basically uniform inner diameter. However, the present invention does not impose any limitation on this. In other embodiments, the liquid passage hole 21 may also be an inclined through hole with an inner diameter that gradually decreases along the refrigerant flow direction, such as... Figure 5B As shown. Or, as... Figure 5C As shown, the liquid passage 21 can be configured as a flanged hole with an arc-shaped inner wall generatrix and a diameter that gradually decreases along the refrigerant flow direction; alternatively, a straight section with a basically constant diameter can be added to the end of the flanged hole, i.e., the inner wall generatrix of the liquid passage is a combination of arc and straight lines. Furthermore, in other embodiments, the liquid passage 21 can also be configured as an arc-shaped bubble hole with the hole wall protruding arc-shaped towards one or both sides of the flow pattern sizing component, such as... Figure 5D and Figure 5E As shown.

[0080] like Figure 2 As shown, the jet hole 31 on the jetting component 3 is a flanged hole whose wall extends towards the direction of the reflective mixing guide plate 4. However, the present invention does not limit this in any way. In other embodiments, the jet hole may also be a through hole with a substantially constant diameter, or a through hole with a diameter that gradually decreases along the refrigerant flow direction (e.g., Figure 6A (As shown). Alternatively, a straight section can be added to the flanged hole, such as... Figure 6B As shown.

[0081] In this embodiment, as Figure 2 and Figure 7 As shown, a mixing cavity 42 with an opening facing the jet hole 31 is formed in the region opposite to the reflecting mixing guide plate 4. The bottom wall of the mixing cavity 42 reflects the refrigerant injected from the jet hole 31. The reflected refrigerant violently collides within the mixing cavity 42, further enhancing the turbulence of the two-phase flow to promote thorough mixing of the refrigerant. In this embodiment, the mixing cavity 42 is a cylindrical chamber with a square longitudinal profile. However, the present invention does not limit this. In other embodiments, the shape of the mixing cavity may also be one or more combinations of a prism with a square longitudinal profile, a frustum or truncated cone with a trapezoidal longitudinal profile, a cone or pyramid with a triangular longitudinal profile, and a partially circular longitudinal profile; such as a combination of a cylinder and a partially spherical shape, a combination of a frustum and a partially spherical shape, a combination of a prism and a partially spherical shape, etc.

[0082] In this embodiment, the reflective mixing guide plate 4 at the mixing cavity 42 extends protruding towards the liquid outlet end of the main body. The downstream surface of the reflective mixing guide plate 4 is a curved structure with a central convex shape. An annular distribution cavity 104 is formed between the downstream surface of the mixing cavity 42 and the inner peripheral wall of the main body 1. This arrangement can reduce the volume of the distribution cavity 104 so that the refrigerant maintains a high-speed dispersed flow pattern and is quickly distributed into multiple liquid distribution holes 14. Furthermore, the vertical distance H between the extended top of the mixing cavity 42 and the inner bottom wall of the liquid outlet end 12 of the main body satisfies: 0 ≤ H ≤ 3 mm. Based on the determined height H0 of the distribution cavity 104 and the inner diameter of the main body 1, the setting of the vertical distance H achieves precise control of the internal volume of the distribution cavity 104, effectively avoiding gas-liquid separation of the dispersed refrigerant due to the distribution cavity 104 being too large, thereby improving the uniformity of refrigerant distribution. Preferably, H is set to 0, that is, the extended tip of the mixing cavity 42 abuts against the inner bottom wall of the liquid outlet end 12 of the main body, such as... Figure 2 As shown. However, the present invention is not limited thereto. In other embodiments, such as Figure 8 As shown, the extended top of the mixing cavity 42 can also be set not to abut the inner bottom wall of the liquid outlet of the body, but in this case, the vertical distance H is also less than or equal to 3mm.

[0083] In this embodiment, as Figure 2As shown, the pre-rectified distributor also includes an inlet pipe 5 welded to the inlet pipe assembly hole 13. The inlet pipe 5 includes a main body section 51 and a jet section 52 sequentially distributed along the refrigerant flow direction. The inner diameter D0 of the main body section 51 remains basically unchanged, while the inner diameter of the jet section 52 is smaller than that of the main body section 51. The jet section 52 accelerates the inlet refrigerant to form a high-speed jet, enhancing the reflected energy of the refrigerant and the flow pattern sculptor 2 to promote the mixing of the gas-liquid two-phase refrigerant in the pre-rectified cavity 101. In the pre-rectified distributor provided in this embodiment, a primary jet is formed at the jet section 52 on the inlet pipe 5, and a secondary jet is formed at the jet hole 31 on the jet sculptor 3. By gradually increasing the refrigerant flow rate, the gravitational influence of the refrigerant during the flow pattern sculpting and uniform distribution process is weakened, so that the refrigerant can always maintain a uniformly mixed diffuse flow pattern. Preferably, the inner diameter D2 at the liquid outlet end of the jet orifice 31 on the jet member 3 is less than or equal to the minimum inner diameter D1 of the jet section 52 on the liquid inlet pipe 5. However, the present invention does not impose any limitation on this.

[0084] In this embodiment, the jet section 52 is a straight section integrally formed with the main body section 51 and whose inner diameter is reduced relative to the main body section 51. The minimum inner diameter D1 of the jet section 52 is the inner diameter of the jet section 52. However, the present invention does not limit this in any way. In other embodiments, a jet orifice plate 53 may be provided in the liquid inlet pipe 5. A jet hole 531 with an inner diameter smaller than the inner diameter D0 of the main body section 51 is formed on the jet orifice plate 53, and the jet section 52 of the liquid inlet pipe is formed at the location of the jet orifice plate 53. In this structure, the minimum inner diameter D1 of the jet section 52 is the minimum diameter of the jet plate hole 531. Specifically, the jet plate hole 531 may be a flanged hole (e.g., Figure 9A As shown), a straight hole with a basically unchanged inner diameter (such as...) Figure 9B (As shown) or any combination of inclined holes. Alternatively, as... Figure 9C As shown, the jet section 52 is configured as a Venturi tube section, and the minimum inner diameter D1 of the jet section 52 is the inner diameter at the straight section of the upper throat of the Venturi tube section. Furthermore, in other embodiments, multiple Venturi tube sections may be provided downstream of the main body of the inlet pipe. In this structure, the inner diameter of the straight throat of the Venturi tube section closest to the inlet pipe assembly hole is used as the minimum inner diameter of the jet section.

[0085] In this embodiment, as Figure 2 and Figure 3As shown, the end of the jet section 52 is welded to the assembly straight section on the inlet pipe assembly hole 13, and the end of the jet section 52 is the outlet end of the inlet pipe 5. However, the present invention does not limit this in any way. In other embodiments, the inlet pipe can also be integrally formed with the body at the location of the inlet pipe assembly hole. Alternatively, for an inlet pipe structure where the jet section 52 is a Venturi tube section, the inlet pipe assembly hole 13 can also be provided as a through hole of a weldless assembly straight section, and a gradually expanding section 54 is formed on the Venturi tube section, located downstream of the throat of the straight section and with an arc-shaped generatrix on its outer wall. The gradually expanding section 54 extends into the pre-rectification cavity 101 through the inlet pipe assembly hole 13, and the outer wall of the gradually expanding section 54 is welded to the inner wall of the inlet end 11 of the body in a surface contact manner, such as Figure 9C As shown.

[0086] like Figure 2 and Figure 10 As shown, on the liquid distribution side of the pre-rectifier distributor, each branch pipe 6 includes a first pipe section 61 and a second pipe section 62 located downstream of the first pipe section 61 with a smaller inner diameter at the downstream end of the first pipe section 61. The difference Δd between the inner diameter d11 at the downstream end of the first pipe section 61 and the inner diameter d12 at the downstream end of the second pipe section 62 is 0.1mm ≤ Δd ≤ 3.5mm. The larger inner diameter of the first pipe section 61 increases the refrigerant flow rate distributed into each branch pipe 6 and reduces the refrigerant distribution resistance, while the relatively smaller inner diameter of the second pipe section 62 can increase the refrigerant flow rate to meet the performance requirements of the downstream heat exchanger components. Based on this, the inner diameter difference Δd precisely controls the degree of refrigerant pressure reduction and acceleration caused by the second pipe section 62, avoiding excessive refrigerant pressure loss due to excessive acceleration.

[0087] Furthermore, a reflective section 611 is formed on the first pipe section 61, extending towards one side of the centerline of the dispensing orifice 14. The axis at the upstream end of the reflective section 611 and the axis at the downstream end of the reflective section 611 intersect to form an angle θ, with 90°≤θ≤175°. The setting of the reflective section 611 makes the second pipe section 62 no longer coaxial with the centerline of the dispensing orifice. When there is a pressure wave downstream and it oscillates upstream, the reflective section 611 reflects and absorbs part of the pressure wave and changes the propagation direction of the remaining pressure wave, causing it to attenuate rapidly. This effectively avoids the influence of the downstream pressure wave on the upstream dispensing orifice 14, thereby further improving the dispensing performance.

[0088] In this embodiment, the branch pipe 6 further includes a branch section 63 welded to the first pipe section 61, and the second pipe section 62 is located on the branch section 63. Specifically, as shown... Figure 10As shown, the upstream end of branch segment 63 is sleeved and connected to the downstream end of the first pipe segment 61, and a second pipe segment 62 with a gradually decreasing inner diameter is formed downstream of the sleeved connection of branch segment 63. However, the present invention does not limit this in any way. In other embodiments, the upstream end of branch segment 63 may also be sleeved and welded to the downstream end of the first pipe segment 61; in this case, the second pipe segment 62 is still a structure with a gradually decreasing inner diameter located downstream of the sleeved connection of branch segment 63, such as... Figure 11A As shown.

[0089] Figure 11B , Figure 11C as well as Figure 11D This is a schematic diagram of the branch pipe provided in another embodiment of the present invention. Figure 11B In the middle, the first pipe section 61, the second pipe section 62, and the branch section 63 are formed as a single unit; Figure 11C In the process, the first pipe section 61 and the second pipe section 62 are integrally formed, while the branch section 63 is welded to the end of the second pipe section 62. Figure 11D In this process, based on the difference in inner diameter between the downstream end of the first pipe section 61 and the upstream end of the branch section 63, a second pipe section 62 is directly formed at the connection between the first pipe section 61 and the branch section 63. Alternatively, multiple second pipe sections can be provided at the downstream end of the first pipe section, and the branch section 63 can be configured as a straight pipe or a bend depending on the actual application.

[0090] Although this embodiment is described using the example of a reflective section 611 formed on the first pipe segment 61, the present invention does not limit this in any way. In other embodiments, the first pipe segment 61 may not need to have a reflective section; in this case, the first pipe segment 61 is a straight pipe, such as... Figure 11E As shown.

[0091] Furthermore, regarding the structure of the second pipe segment 62, in other embodiments, the second pipe segment 62 may also include a tapered section and a maintaining straight section located downstream of the tapered section and having a certain length L62. The inner diameter of the maintaining straight section is close to the inner diameter at the downstream end of the tapered section and remains substantially unchanged within the length L62. Figure 11F As shown. Alternatively, an orifice plate 66 can be added at the flared connection of the first pipe section 61 or branch section 63, using the through holes 661 on the orifice plate 66 to accelerate the refrigerant flow; in this case, the pipe section where the orifice plate 66 is located is the second pipe section 62, as shown. Figure 11G As shown.

[0092] On the other hand, this embodiment also provides a heat exchanger assembly including the aforementioned pre-rectified distributor.

[0093] On the other hand, this embodiment also provides a refrigeration device, which includes the above-described heat exchanger assembly.

[0094] Example 2

[0095] This embodiment is basically the same as Embodiment 1 and its variations, except that the structure of the flow pattern finishing component 2 is different. For example... Figure 12 and Figure 13 As shown, a finishing cavity 22 with an opening facing the inlet pipe assembly hole 13 is formed on the area of ​​the flow pattern finishing member 2 opposite to the flow inlet pipe assembly hole 13. The flow pattern finishing member 2 at the finishing cavity 22 protrudes and extends towards the side where the jet member 3 is located. The downstream surface of the flow pattern finishing member 2 is a curved structure with a central convex shape. In this structure, the flow pattern maintaining cavity 102 refers to the chamber enclosed by the downstream surface of the curved flow pattern finishing member 2 and the upstream surface of the jet member 3, such as... Figure 13 The cavity enclosed by the line drawn at the midpoint.

[0096] Compared to Embodiment 1, this embodiment enhances the pre-rectification effect by providing a rectification cavity 22 on the flow pattern sizing component 2. Specifically, the refrigerant with an asymmetrical flow pattern is injected into the rectification cavity 22. After being reflected by the bottom wall of the rectification cavity 22, it violently collides within the cavity 22 to disperse the liquid refrigerant into droplets. During the maximum kinetic energy phase after reflection, the rectification cavity 22 provides a mixing space for the refrigerant, enhancing the degree of turbulence to promote gas-liquid two-phase mixing. Simultaneously, when the mass flow rate and velocity of the input refrigerant are large, the arrangement of the rectification cavity 22 can effectively reduce the impact of the reflection force on the input refrigerant, avoiding refrigerant backflow in the inlet pipe caused by excessive reflection force.

[0097] In this embodiment, the tidying cavity 22 is a cylindrical chamber with a square longitudinal section profile, where the longitudinal section refers to the section along the depth direction of the tidying cavity. However, the present invention does not limit this in any way. In other embodiments, the shape of the tidying cavity 22 may also be a prism with a square longitudinal section profile, a frustum of a cone with a trapezoidal longitudinal section profile, or a frustum of a pyramid (e.g., Figure 14A ), a cone or pyramid with a triangular longitudinal profile (such as Figure 14B And the longitudinal section outline is partially circular (i.e. partially spherical, such as...) Figure 14C One or more combinations of ) . Such as a combination of cylindrical and partially spherical shapes (e.g. Figure 14D (as shown), combinations of frustums and partial spheres, combinations of prisms and partial spheres, etc.

[0098] Example 3

[0099] This embodiment is basically the same as Embodiment 2 and its variations, except that a partition 7 is provided inside the flow pattern maintaining cavity 102.

[0100] As described in Embodiment 2, the arrangement of the arranging cavity 21 on the flow pattern arranging component 2 allows the reflected refrigerant to participate in mixing with maximum kinetic energy, thereby increasing the turbulence of the two-phase flow. However, due to the limitations of the depth of the arranging cavity 21 and the inner diameter of the body 1, the volume of the flow pattern maintaining cavity 102 may be relatively large. The initial diffuse flow formed after the pre-rectification cavity 101 enters the excessively large flow pattern maintaining cavity 102, which is very likely to cause gas-liquid two-phase separation again due to over-expansion.

[0101] To solve this problem, such as Figure 15 and Figure 16 As shown, the pre-rectified distributor also includes a partition 7 disposed between the flow pattern shaping member 2 and the jetting member 3. The partition 7 divides the flow pattern maintaining chamber 102 into a first maintaining chamber 1021 and a second maintaining chamber 1022, and a plurality of partition holes 71 are formed on the partition 7 to connect the first maintaining chamber 1021 and the second maintaining chamber 1022. Figure 15 (Due to viewing angle, not shown) The volumes V1 of the pre-rectifying cavity 101, V21 of the first sustaining cavity 1021, and V22 of the second sustaining cavity 1022 satisfy the following conditions: 0.75 ≤ V1 / V21 ≤ 1.3, 0.75 ≤ V21 / V22 ≤ 1.3. The partition 7 precisely controls the expansion of the refrigerant as it flows through adjacent chambers, ensuring that the refrigerant develops into a stable, dispersed flow pattern after flowing through the first sustaining cavity 1021 and the second sustaining cavity 1022.

[0102] In this embodiment, as Figure 17 As shown, a clearance hole 72 is formed on the partition 7 opposite to the finishing cavity 22, and the partition 7 is sleeved around the outer periphery of the finishing cavity 22 through the clearance hole 72. At this time, the first maintaining cavity 1021 is an annular cavity surrounding the finishing cavity 22, formed by the downstream surface of the flow-shaped finishing member 2 and the upstream surface of the partition 7, as shown. Figure 16 The area indicated by the dashed line. The second maintaining cavity 1022 is the chamber enclosed by the downstream surface of the flow pattern sizing element 2, the downstream surface of the partition 7, and the upstream surface of the jet element 3 at the sizing cavity 22, as shown below. Figure 16 The area indicated by the dashed line. However, this invention does not limit this area in any way.

[0103] In this embodiment, the plurality of baffle holes 71 on the baffle 7 are staggered with the plurality of liquid passage holes 21 on the flow pattern finishing member 2. Figure 17AThe dashed line indicates the projected position of the liquid passage hole on the baffle 7. This arrangement ensures that the refrigerant after initial rectification in the pre-rectification chamber 101 does not flow directly to the second maintenance chamber 1022, but instead, after mixing and developing in the first flow-type maintenance chamber 1021, it enters the second flow-type maintenance chamber 1022 through multiple baffle holes 71 for further mixing and development. Similarly, to avoid excessive pressure loss caused by excessive throttling of the baffle holes, the sum of the flow areas S2 of the multiple baffle holes 71 is set to satisfy the following condition with respect to the internal cavity cross-sectional area S02 of the body where the baffle is located: 0.1 ≤ S2 / S02 ≤ 0.45.

[0104] Figure 18A The diagram shown is a schematic representation of the pre-rectifier distributor after removing the inlet pipe and branch pipe according to another embodiment of the present invention. In this structure, the baffle 7 has a closed structure opposite to the rectifier cavity 22, and the baffle 7 is basically attached to the outer bottom surface of the rectifier cavity 22; at this time, the second maintaining cavity 1022 is a chamber enclosed by the downstream surface of the baffle 7 and the upstream surface of the jet component 4, as shown in the figure. Figure 18A The chamber marked 1022 is enclosed by the dashed line. In other embodiments, such as... Figure 18B As shown, a partition 7 can also be set downstream of the tidying cavity 22, with the partition 7 protruding upstream from the tidying cavity 22 to fit against the outer bottom surface of the tidying cavity 22.

[0105] Although this embodiment is described using the example of a finishing cavity 22 formed on the flow pattern finishing member 2, the present invention does not limit this in any way. In other embodiments, when the flow pattern finishing member has other structures, a partition can be added to divide the flow pattern maintaining cavity 102 into a first maintaining cavity 1021 and a second maintaining cavity 1022. Figure 18C The diagram shows an example of adding a partition to the pre-rectified distributor (the flow pattern rectifier is a plate structure with both sides nearly planar) provided in Embodiment 1 to divide the flow pattern maintaining chamber 102 into a first maintaining chamber 1021 (e.g., Figure 18C The chamber enclosed by the midpoint line) and the second maintenance chamber 1022 (as shown) Figure 18C The cavity enclosed by the dotted line.

[0106] Example 4

[0107] This embodiment is basically the same as Embodiment 1 and its variations, except that the structure of the reflective mixing guide plate 4 is different.

[0108] like Figure 19As shown, in this embodiment, the downstream surface of the reflective mixing guide plate 4 is nearly planar. The pre-rectifying distributor also includes a flow channel forming member 8 disposed within the flow distribution cavity 104 and located on the inner periphery of the plurality of liquid distribution holes 14. The flow channel forming member 8 is a rotating member that protrudes from the inner bottom wall of the liquid outlet end 12 of the body towards the direction of the reflective mixing guide plate 4 and rotates around the axis of the body 1. The flow channel forming member 8 and the inner peripheral wall of the body 1 form an annular flow channel connecting the plurality of liquid distribution holes, and the cross-section of the flow channel forming member remains basically unchanged or gradually decreases with the extension direction.

[0109] Similar to the reflective mixing guide plate 4 at the mixing cavity 42 in Embodiment 1, which protrudes towards the liquid outlet end of the body, the flow channel forming member 8 in this embodiment can reduce the volume of the distribution cavity 104 to avoid gas-liquid separation of the mixed homogeneous refrigerant within the distribution cavity 104. Simultaneously, the annular flow channel formed by the flow channel forming member 8 and the inner peripheral wall of the body 1 can also guide the homogeneous refrigerant, enabling it to be evenly distributed into the multiple annularly distributed liquid distribution holes 14 to achieve symmetrical refrigerant distribution.

[0110] like Figure 19 As shown, the flow channel forming member 8 is a cone with a cross-section that gradually decreases in size along its extension direction. The vertical distance H1 from the extended tip of the flow channel forming member 8 to the downstream surface of the reflective mixing guide plate 4 satisfies: 1mm ≤ H1 ≤ 2H0 / 3, where H0 is the height of the flow splitting cavity. However, the present invention does not impose any limitations on this. In other embodiments, such as Figure 20 As shown, the flow channel forming member 8 can also be a cylindrical spacer with a cross-section that remains substantially unchanged along its extension direction, and the extended top end of the spacer abuts against the reflective mixing guide plate 4 region within the inner periphery of the plurality of guide holes 41. In other embodiments, the flow channel forming member can also be a combination of a cone and a spacer.

[0111] Example 5

[0112] This embodiment is basically the same as Embodiment 4 and its variations, except that the pre-rectified distributor provided in this embodiment does not have a reflective mixing guide plate 4.

[0113] like Figure 21As shown, the pre-rectifying distributor includes a body 1 and a flow pattern sculptor 2, a jetting component 3, and a flow channel forming component 8, which are sequentially arranged within the body's accommodating cavity along the refrigerant flow direction. The liquid inlet end 11 of the body has a liquid inlet pipe assembly hole 13, and its liquid outlet end 12 has multiple liquid distribution holes 14. The flow pattern sculptor 2 and the liquid inlet end 11 of the body form a pre-rectifying cavity 101, and the flow pattern maintaining cavity 102 is formed between the flow pattern sculptor 2 and the jetting component 3. The flow pattern sculptor 2 has multiple liquid passage holes 21 connecting the pre-rectifying cavity 101 and the flow pattern maintaining cavity 102, and these holes 21 are distributed around the outer periphery of the projection area of ​​the liquid inlet pipe assembly hole 13 on the flow pattern sculptor 2. The jetting component 3 has a jetting hole 31 connecting the flow pattern maintaining cavity 102, and the jetting hole 31 is opposite to the projection area of ​​the liquid inlet pipe assembly hole 13 on the flow pattern sculptor 2. The flow channel forming member 8 is disposed between the jet member 3 and the liquid outlet end 12 of the body and is located on the inner periphery of multiple liquid distribution holes 14. The flow channel forming member 8 is a rotating member that extends from the inner bottom wall of the liquid outlet end 12 of the body towards the direction of the jet member 3 and rotates around the axis of the body 1. The jet member 3, the flow channel forming member 8 and the liquid outlet end 12 of the body form an annular flow distribution cavity 104' that connects multiple liquid distribution holes 14. The cross-section of the flow channel forming member 8 remains basically unchanged or gradually decreases with the extension direction.

[0114] Similarly, the pre-rectified distributor provided in this embodiment uses a flow pattern sculptor 2 and a jetting component 3 to tidy up the asymmetric flow at the inlet, so that the refrigerant flow pattern gradually develops into a uniformly mixed, dispersed flow pattern. To ensure that the refrigerant flow pattern develops into a stable, dispersed state and maintains this uniformly mixed flow pattern throughout the subsequent distribution process, the pre-rectified cavity volume V1, the flow pattern maintaining cavity volume V2, and the annular splitting cavity volume V4' are set to satisfy the following: 0.6 ≤ V1 / V2 ≤ 1.5, 0.6 ≤ V2 / V4' ≤ 1.5.

[0115] Similarly, in other embodiments, when the volume of the flow pattern maintaining cavity 102 is large, a partition can be added inside the flow pattern maintaining cavity to divide the large-volume flow pattern maintaining cavity into a first flow pattern maintaining cavity and a second flow pattern maintaining cavity with smaller volumes.

[0116] In summary, the pre-rectified distributor provided by this invention features a flow pattern sculptor on the side of the internal cavity near the liquid inlet. This flow pattern sculptor reflects the gas-liquid two-phase separated refrigerant input from the liquid inlet, breaking the liquid film into droplets to promote gas-liquid mixing. Simultaneously, the refrigerant reflection stream and incident stream, moving in opposite directions, create turbulence within the pre-rectified cavity enclosed by the flow pattern sculptor and the liquid inlet of the main body, enhancing the turbulence of the two-phase flow and causing the refrigerant to gradually develop into a dispersed flow pattern. The pre-rectified refrigerant enters the flow pattern maintenance cavity, where it is fully mixed and develops before converging at the jet orifice on the jetting element. The jet orifice reduces the pressure and increases the speed of the refrigerant flow, increasing the refrigerant velocity so that the liquid refrigerant has sufficient inertial force to overcome gravity during subsequent distribution, preventing gas-liquid two-phase segregation from recurring in the fully mixed dispersed flow pattern and improving the uniformity of refrigerant distribution. Furthermore, by precisely controlling the volume ratio of the pre-rectification cavity, the flow pattern maintenance cavity, and the reflection mixing cavity within the main body, the refrigerant can fully develop into a stable diffuse flow pattern in the flow pattern maintenance cavity and maintain this flow pattern throughout the distribution process after jetting, thereby significantly improving the distribution performance of the distributor.

[0117] The pre-rectified distributor provided by this invention pre-rectifies the inlet refrigerant flow pattern by incorporating a flow pattern rectifier within the main body, thereby reducing the impact of the refrigerant inlet flow pattern on the distribution performance. This distributor structure eliminates the need for any adjustments to the inlet pipe, greatly simplifying the processing, installation, and welding of the inlet pipe, and significantly improving the distributor's applicability to ensure compatibility with various refrigeration equipment of different specifications.

[0118] Although the present invention has been disclosed above by way of preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art may make some modifications and refinements without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be determined by the scope of protection claimed in the claims.

Claims

1. A pre-rectified distributor, characterized in that, include: The main body and the flow pattern sizing component, jet component and reflective mixing guide plate are sequentially arranged in the inner cavity of the main body along the refrigerant flow direction; The main body has an inlet pipe assembly hole on its inlet end and multiple liquid distribution holes on its outlet end. The flow pattern sizing component is configured to form a pre-rectification cavity with the liquid inlet end of the main body and to form a flow pattern maintenance cavity with the jet component. The flow pattern sizing component has multiple liquid passage holes that connect the pre-rectification cavity and the flow pattern maintenance cavity, and the multiple liquid passage holes are distributed on the outer periphery of the projection area of ​​the liquid inlet pipe assembly hole on the flow pattern sizing component. A jetting component has a jetting hole that communicates with a flow pattern maintaining cavity, and the jetting hole is opposite to the projection area of ​​the liquid inlet pipe assembly hole on the flow pattern finishing component; The reflective mixing guide plate is configured to form a reflective mixing cavity that connects to the jet orifice between itself and the liquid outlet end of the main body, and to form a flow distribution cavity between itself and the liquid outlet end of the main body. The reflective mixing guide plate has multiple guide holes that correspond one-to-one with the multiple liquid distribution holes and are respectively connected to the reflective mixing cavity and the flow distribution cavity. The multiple guide holes are distributed in a ring around the axis of the main body on the outer periphery of the projection area of ​​the jet orifice on the reflective mixing guide plate.

2. The pre-rectified distributor according to claim 1, characterized in that, The pre-rectification cavity volume V1, the flow pattern maintenance cavity volume V2, and the reflection mixing cavity volume V3 satisfy the following conditions: 0.6≤V1 / V2≤1.5, 0.6≤V2 / V3≤1.

5.

3. The pre-rectified distributor according to claim 1, characterized in that, On the flow pattern finishing component, a finishing cavity with an opening facing the liquid inlet pipe assembly hole is formed in the area opposite to the liquid inlet pipe assembly hole. The longitudinal cross-sectional outline of the finishing cavity is one or more combinations of square, trapezoidal, triangular or partially circular. Alternatively, the flow pattern finishing component may be a plate structure in which both the upstream and downstream surfaces are nearly planar.

4. The pre-rectified distributor according to claim 3, characterized in that, The flow-shaped finishing element at the finishing cavity protrudes and extends towards the side where the jet element is located.

5. The pre-rectified distributor according to claim 1, characterized in that, The pre-rectified distributor also includes a partition disposed between the flow pattern rectifier and the jetting component. The partition divides the flow pattern maintaining cavity into a first maintaining cavity and a second maintaining cavity. The partition has a plurality of partition holes that connect the first maintaining cavity and the second maintaining cavity. The pre-rectified cavity volume V1, the first maintaining cavity V21 and the second maintaining cavity V22 satisfy the following conditions: 0.75≤V1 / V21≤1.3, 0.75≤V21 / V22≤1.

3.

6. The pre-rectified distributor according to claim 5, characterized in that, The multiple baffle holes and the multiple liquid passage holes on the flow pattern finishing component are staggered. The sum of the flow areas of the multiple baffle holes, S2, and the cross-sectional area of ​​the inner cavity of the body where the baffle is located, S02, satisfy the following condition: 0.1≤S2 / S02≤0.

45.

7. The pre-rectified distributor according to claim 5, characterized in that, On the flow pattern finishing member, the area opposite to the liquid inlet pipe assembly hole protrudes and extends towards the side where the jet member is located to form a finishing cavity with an opening facing the liquid inlet pipe assembly hole. A clearance hole is formed on the partition plate opposite to the finishing cavity, and the partition plate is sleeved on the outer periphery of the finishing cavity through the clearance hole. Alternatively, the partition plate may have a closed structure opposite to the tidying cavity, with the partition plate essentially fitting against the outer bottom surface of the tidying cavity.

8. The pre-rectified distributor according to claim 1, characterized in that, The sum of the flow areas S1 of multiple liquid passage holes on the flow pattern rectifier and the cross-sectional area S01 of the body cavity where the flow pattern rectifier is located satisfy the following condition: 0.1≤S1 / S01≤0.

45.

9. The pre-rectified distributor according to claim 1, characterized in that, The liquid passage holes on the flow pattern finishing component and the flow guide holes on the reflective mixing guide plate are all through holes; the jet holes on the jet component are through holes.

10. The pre-rectified distributor according to claim 1, characterized in that, On the reflective mixing guide plate, a mixing cavity with an opening facing the jet hole is formed in the area opposite to the jet hole. The longitudinal cross-sectional profile of the mixing cavity is one or more combinations of square, trapezoidal, triangular or partially circular.

11. The pre-rectified distributor according to claim 10, characterized in that, The reflective mixing guide plate at the mixing cavity protrudes and extends towards the liquid outlet end of the main body, and an annular flow divider is formed between the downstream surface of the mixing cavity and the inner peripheral wall of the main body.

12. The pre-rectified distributor according to claim 11, characterized in that, When the longitudinal profile of the mixing cavity is square or trapezoidal, the vertical distance H from the extended top of the mixing cavity to the inner bottom wall of the liquid outlet of the main body satisfies: 0≤H≤3mm.

13. The pre-rectified distributor according to claim 1, characterized in that, The downstream surface of the reflective mixing guide plate is close to a plane. The pre-rectified distributor also includes a flow channel forming member disposed in the flow distribution cavity and located on the inner periphery of multiple liquid distribution holes. The flow channel forming member is a rotating member that protrudes from the inner bottom wall of the liquid outlet end of the body towards the direction of the reflective mixing guide plate and rotates around the axis of the body. The flow channel forming member and the inner peripheral wall of the body form an annular flow channel that connects multiple liquid distribution holes. The cross-section of the flow channel forming member remains basically unchanged or gradually decreases with the extension direction.

14. The pre-rectified distributor according to claim 13, characterized in that, The flow channel forming element is a spacer with a cross-section that remains essentially unchanged along its extension direction, and the extended top of the spacer abuts against the reflective mixing guide plate area on the inner periphery of multiple guide holes.

15. The pre-rectified distributor according to claim 13, characterized in that, The cross-section of the flow channel forming member gradually decreases along its extension direction. The vertical distance H1 from the extended top of the flow channel forming member to the downstream surface of the reflective mixing guide plate satisfies: 1mm≤H1≤2H0 / 3, where H0 is the height of the flow splitting cavity.

16. The pre-rectified distributor according to claim 1, characterized in that, The pre-rectified distributor also includes an inlet pipe welded to the inlet pipe assembly hole, the inlet pipe including a main body section with a basically unchanged inner diameter and a jet section located downstream of the main body section with a smaller inner diameter than the main body section.

17. The pre-rectified distributor according to claim 16, characterized in that, The inner diameter of the liquid outlet end of the jetting orifice on the jetting component is less than or equal to the minimum inner diameter of the jetting section on the inlet pipe.

18. The pre-rectified distributor according to claim 16, characterized in that, A jet orifice plate is provided inside the liquid inlet pipe. The jet orifice plate has jet orifice holes with an inner diameter smaller than that of the main body section and the jet orifice holes are through holes. The location of the jet orifice plate forms the jet section of the liquid inlet pipe. Alternatively, the jet section is a Venturi tube section, with the throat of the Venturi tube section being the point of minimum inner diameter of the jet section. Alternatively, the jet section may be a straight section with a reduced inner diameter relative to the main body section.

19. The pre-rectified distributor according to claim 1, characterized in that, The pre-rectified distributor also includes multiple branch pipes welded to multiple dispensing holes. Each branch pipe includes a first pipe section and a second pipe section located downstream of the first pipe section with a smaller inner diameter than the downstream end of the first pipe section. The difference Δd between the inner diameter d11 at the downstream end of the first pipe section and the inner diameter d12 at the downstream end of the second pipe section is: 0.1mm≤Δd≤3.5mm.

20. The pre-rectified distributor according to claim 19, characterized in that, The first pipe section has a reflective section that bends and extends to one side relative to the center line of the liquid distribution hole. The axis at the upstream end of the reflective section and the axis at the downstream end of the reflective section intersect to form an angle θ, and 90°≤θ≤175°. Based on the reflective section, the axis of the second pipe section intersects the center line of the liquid distribution hole. Alternatively, the first pipe section may be a straight pipe.

21. The pre-rectified distributor according to claim 19, characterized in that, Each pipe also includes a branch section. The second pipe section is a tapered structure that is integrally formed with the first pipe section and has a gradually decreasing inner diameter. The branch section is welded to the second pipe section, or the first pipe section, the second pipe section and the branch section are integrally formed. Alternatively, the branch segment may be sleeved and welded to the first pipe segment, and the sleeved and welded joint between the two forms the second pipe segment; Alternatively, the branch segment is welded to the first pipe segment, and the second pipe segment is formed from the branch segment.

22. A pre-rectified distributor, characterized in that, include: The main body and the flow pattern arranging component, jetting component and flow channel forming component are sequentially arranged in the main body cavity along the refrigerant flow direction; The main body has an inlet pipe assembly hole on its inlet end and multiple liquid distribution holes on its outlet end. The flow pattern sizing component is configured to form a pre-rectification cavity with the liquid inlet end of the main body and to form a flow pattern maintenance cavity with the jet component. The flow pattern sizing component has multiple liquid passage holes that connect the pre-rectification cavity and the flow pattern maintenance cavity, and the multiple liquid passage holes are distributed on the outer periphery of the projection area of ​​the liquid inlet pipe assembly hole on the flow pattern sizing component. The jetting component has a jetting hole that connects to the flow pattern maintenance cavity, and the jetting hole is opposite to the projection area of ​​the liquid inlet pipe assembly hole on the flow pattern finishing component. A flow channel forming component is disposed between the jet component and the liquid outlet end of the main body and located within the inner circumference of multiple liquid distribution holes. The flow channel forming component is a rotating component that extends from the inner bottom wall of the liquid outlet end of the main body toward the direction of the jet component and rotates around the axis of the main body. The jet component, the flow channel forming component, and the liquid outlet end of the main body form an annular flow distribution cavity that connects multiple liquid distribution holes. The cross-section of the flow channel forming component remains basically unchanged or gradually decreases with the extension direction.

23. The pre-rectified distributor according to claim 22, characterized in that, The pre-rectification cavity volume V1, the flow pattern maintenance cavity volume V2, and the annular split cavity volume V4' satisfy the following conditions: 0.6≤V1 / V2≤1.5, 0.6≤V2 / V4'≤1.

5.

24. The pre-rectified distributor according to claim 23, characterized in that, The pre-rectified distributor further includes a partition disposed between the flow pattern sizing component and the jet component. The partition divides the flow pattern maintaining chamber into a first maintaining chamber and a second maintaining chamber. The partition has a plurality of partition holes that connect the first maintaining chamber and the second maintaining chamber, and the plurality of partition holes are staggered with the plurality of liquid passage holes on the flow pattern sizing component. The volumes of the pre-rectified chamber V1, the first maintaining chamber V21, and the second maintaining chamber V22 satisfy the following: 0.75≤V1 / V21≤1.3, 0.75≤V21 / V22≤1.

3.

25. A heat exchanger assembly, characterized in that, Includes the pre-rectified distributor according to any one of claims 1 to 24.

26. A refrigeration device, characterized in that, Includes the heat exchanger assembly as described in claim 25.

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